Roll feed



July 4, 1961 Filed lay 7, 1959 B. v. MALMBERG 2,990,722

Rou. Fm

3 Sheets-Sheet 1 July 4, 1961 B. v. MALMBERG 2,990,722

ROLL FEED Filed May '7. 1959 3 sneets-sheet 2 IN V EN TOR.

//ameys July 4, 1961 B. v. MALMBERG ROLL FEM) 3 Sheets-Sheet 3 Filed lay '7. 1959 vUnited States Patent C)j 2,990,722 ROLL FEED Bror V. Malmberg, 4426 Soo Line Lane, Schiller Park, Ill.

` Filed May 7, 1959, Ser. No. 811,745

13 Claims. V(Cl. 74-121) This invention relates to a device for varying the length i ,to the start of its operation. These adjustments are usual- 1y coarse adjustments and the machine must be stopped and started many times before the operator has his machine set for the proper feed. This trial and error method of arriving at the proper speed for the roll feed' is a time waster. In my invention I have provided a means for making a fine adjustment to` the length of feed of a roll feed while the machine is in operation. The coarse 'adjustment is made to prior to starting of the machine and then a fine adjustment is made to the machine while it is Operating.

One purpose of my invention is to provide a fine speed adjustment for a roll feed or the like.

Another purpose is to provide a fine adjustment for a roll feed which may be used to adjust the length of feed during operation.

Another purpose is to provide a roll feed in which a coarse feed adjustment is made prior to operation and a fine feed adjustment is made during operation.

Other purposes will appear in the ensuing specification, drawings and claims.

The invention is illustrated diagrammatically in the following drawings wherein:

FIGURE 1 is a front view of a roll feed with parts cut away;

.FIGURE 2 is a top plan view of |a fine speed adjustment mechanism used in the roll feed of FIGURE 1;

FIGURE 3 is a section taken along line 3-3 of FIG- URE 2; i

FIGURE 4 is a section taken along the line 4-4 of 'FIGURE 3;

'FIGURE 5 is a plan view of a lost motion connection `used in the fine speed' adjustrnentmechanism of FIG- URE 3;

FIGURE 6 is a -plan view of the lost motion connection of FIGURE 5, rotated 90.

Referring now to FIGURE 1, 10 ndioates a suitable base upon which a roll feed mechanism indicatedgenerally at 12 is mounted. It is important in any machine tool that the material be fed into the machine at the 'proper speed. In my roll feed the material is moved by in changing the point at which the drive rod 20 is secured to the eccentric 16 as this changes the longitudinal distance that rack bar 22 wi-ll move. As shofwn in the drawings the drive rod is positioned near the top of the eccentric, however, the drive rod may be positioned at any point 1 along groove 24 in the eccentric 16 by loosening nut 26 and changing the position at which the rod is secured.

`clutch member.

Patented July 4, 1961 The details of the coarse adjustment of the roll feed have not been described in detail 'as they are conventional in the art. V

The fine feed adjustment which is shown in FIGURE 2 is ndcated generally at 28 in FIGURE l.` Movement of rack bar 22 is transforrned by the fine adjustment into rotation of shaft 14. In FIGURE 2 a conventional rack and clutch housing 30 has a micrometer dial 32 positioned at one end. Movement of this dial provides the fine feed control. The rack 22 is adapted to move through a generally square opening 34 positioned near the opposite end of the housing 30. A gear housing 36 is positioned at this same end of the housing 30.

FIGURE 3 shows the details of both housings. Longitudinal movement of the rack bar '22 causes lrotation of gear 38 which is keyed at 40 to a clutch body 42. The clutch body 42 is freely rotatable on drive shaft 44 as there are bearings 46 interposed between the clutch bod and the drive shaft.

A clutch spider 48 is mounted on drive shaft 44 and has a portion 50 which underlies a portion of the clutch body 4'2. A cap 512 overlies a portion of the spider and is secured by means of cap screws 54 to the clutch body.

FIGURE 4 shows the details of the connection between the clutch spider and the clutch body. The portion 50 of the clutch spider underlying the clutch body has a plurality of grooves 56 spaced around its outer circumference. Each of these grooves contain a clutch roller 58 which abuts a plunger 60 biased towards the roller by means of a spring 62. When the rack bar 22 moves the gear 38 this causes rotation of the clutch body. When the clutch body moves in the direction of arrow 63 the clutch rollers are forced in between the grooves 56 and the inside of the clutch body and will cause rotation of the spider in the direction of arrow 63. When gear 38'and the clutch body move in the opposite direction the clutch rollers 58 will be forced down against the plungers and 'will force the plungers into bores 64 against the action of the springs 62. This will not cause rotation of the clutch spider as the rollers will move against the plungers and will be free to rotate in the grooves. When |gear 38 moves in this direction then, the clutch -body rotates without the spider.

The portion 68 of the clutch spider which is 'adjacent 45 'clutch member 70 has a plurality, in this case two, axial grooves 72. This is clearly shown in FIGURE 5. The grooves 72 have tapered side walls 74 and are adapted to receive projections 76 which extend outward from the clutch member 70. The projections 76 have tapered side walls 77 which have the same contour or shape as the side walls 74. As can clearly be seen in FIGURE 5 the projections 76 may be received Vat various depths within the grooves 72. The actual extent to which the projections are received Within the grooves is govemed by springs 80 which are placed between the clutch spider `and clutch member and by the micrometer dial 32.

When the clutch spider rotates it will also rotate the However rotation of the clutch member will not begin at the'precise moment that rotation of the clutch spider begins. This is due to the lost motion con- This lost motion connection consists of the projections and the grooves hereinbefore described. The amount or degree of lost motion between these two members is dependent upon the extent or the depth to which the prog'ections are received in the grooves. In other words, if the projections 76 are completely received within the grooves 72 there will be no lost motion between the spider and the clutch body whereas when the projections are not completely received vvithin the grooves there is space 82 between these two members and this space must be angularly traversed before there Will be actual mechanical connection 2,99o,722 W e ff between the clutch body and the clutch spider. The size of this space or the degree of lost motion may be controlled by the micrometer dial 32.

The dial 32 is threadedly engaged with a projecting portion of rack and clutch housing cover 30aso that rotation of the dial causes inward movement of pins 84. These pins abut thrust bearing cap 86 which in turn is seated on thrust 'bearing 88. The thrust bearing is seated on -an annular shoulder 90 on the clutch member. Therefore, movement of the micrometer dial either inwardly or outwardly Will cause the pins 84 to either move the clutch member toward the clutch spider or away from it. This movement of course chang the extent to which projections 76 are lreceived within the grooves 72. The clutch member is normally biased outward by the springs 80.

The drive shaft 44 extends through the clutch member and is splined thereto as at 92. The drive shaft 44 is free to rotate in the 'housing cover '30a as it is supported within the housing cover by bearing 94.

The rack and clutch housing also includes a second cover 301) which is secured to the housing 30 by means of screws 31. Screws 31a secure cover 30a to the housing. The housing is completed by `grease seals 95.

Drive shaft 44 extends through the gear housing 36 and has a helical gear 96 keyed thereto. This helical gear is adapted to drive the shaft 14. Roller bearings 98 support the drive shaft 44 within the gear housing 36. As was the case in the housing 30, the gear housing 36 is completed by a pair of covers 36a and '36b which are secured by means of screws 35a and 35h to the housing. Grease seals 100 complete the structure.

The use, operation and function of the invention are as follows:

The invention shown and described herein is directed to a means for making micrometric adjustments in the length of feed of a roll feed while it is in operation. The usual roll feed is used to feed material into a punch press or other machine tool and it must be set so that material will be fed into the machine at the proper rate. The coarse adjustment for the roll feed comprises an eccentric to which is secured a drive rod 20. The position of the drive rod 20 on the eccentric determines the longitudinal distance through which the drive rod and the rack bar secured thereto will move past the gear 38. As the rack bar moves up and down past gear 38 it causes rotation of this gear. This in turn causes rotation of the clutch body to which the gear is keyed. The clutch body is connected to a clutch `spider in such a manner that the clutch spider will rotate only when rotation of the clutch 'body is in one direction. For purposes of illustration assume that the clutch spider will only rotate when the vrack bar is moving down. In other words, when the rack moves down it causes rotation of gear 38 in one direction, this being the direction indicated by arrow 63. Rotation of the clutch spider in this direction will cause rotation of the clutch member, this in turn causing rotation of drive shaft -44 which rotates shaft 14. The shaft 14 is the feed roll shaft and it is -rotation of this shaft that causes movement of the material through the machine. Shaft 14 Will only rotate when drive shaft 44 rotates and this will only rotate when the clutch spider and clutch member rotate. As described above there will only be rotation of the clutch spider when the rack bar is moving down.

In order to make a fine adjustment to the length of feed it is necessary to vary the time during which shaft 14 rotates. This is set by the duration of rotation of drive shaft 44. Shaft 44 only rotates when there is contact between the clutch member and the clutch spider. This length of time is controlled by the lost motion connection between these two elements which consists in the projections of the clutch member and` the grooves formed in the spider. In order to vary the depth to which the projections are received within the grooves 4 V which varies the length of time that shaft 44 rotates, the operator turns micrometer dal 32 so that it moves the clutch member toward or away from the clutch spider.

When the clutch spider starts to rotate, a small instant of time will elapse before it contacts the projection on the clutch member. Thefi instant of time may be varied by the depth to` which the projection is received within the groove. This is a lost motion connection and it is the fine adjustment for my roll feed. The deeper the projection is received within the grooves the longer the period of time during which the drive shaft '44 will rotate. Drive shaft 44 never rotates `as illustrated herein during the upward stroke of the rack bar. However it does rotate on the downward stroke during that period of time in which the clutch member and the clutch spider are engaged.

In practice, when the clutch body rotates in the direction of arrow `63 the rollers 58 are tightly held in the grooves 56 between the clutch body and the clutch spider, thus turning the clutch spider in the direction of the arrow. When the clutch body rotates in the opposte direction there is, at first, some slight movement of the clutch spider in the same direction as the clutch spider must move a small amount to free the rollers 58. The amount of movement of the clutch spider is suflicient to move it out of contact with the projections on the clutch member, thus providing for lost motion between the clutch spider and the clutch member on the next stroke of the rack bar.

There are numerous substitutions and alterations coming within the scope of the invention. For example, in some applications drive shaft 44 is not necessary as the shaft 14, which controls the rate at which material is fed to the machine tool or the like, could be driven directly by the clutch member. Additionally the rack bar might be replaced by a gearing arrangement which would cause rotation of the gear 38 in two diiferent directions. Rotation of this gear in two different directions is What is important to the operation of this device.

Whereas I have described and illustrated one form of the invention it should be realized that there are many modifications coming within the scope and spirit thereof and we therefore only wish to be limited by the following claims.

I claim:

1. In a roll feed, a drive shaft rotation of which moves material through said roll feed, a clutch member mounted on said shaft for rotation therewith, a gear freely reciprocal around said shaft, means for reciprocating said gear including a coarse adjustment for controlling the motion thereof, means for transferring motion of said gear in one direction through said clutch member to said drive shaft including a lost motion connection, and a fine adjustment for controlling motion of said drive shaft including means for adjusting the degree of lost motion while said roll feed is Operating.

2. In a roll feed, 'a drive shaft rotation of which moves material through said roll feed, a clutch member mounted on said shaft for rotation therewith, a clutch body freely reciprocal around said shaft, a clutch spider mounted on said shaft adjacent said clutch member, -a gear mounted on and secured to said clutch body, means for reciprocating said gear including a coarse adjustment for controlling the motion thereof, said clutch spider and said clutch body being interconnected whereby reciprocation of said gear and said clutch body in one direction rotate said spider, a lost motion connection between said spider and said clutch member whereby part of the movement of said spider is transferred to said shaft, and a fine adjustment for controlling motion of said drive shaft including a means for vadjusting the degree of lost motion while said roll feed is Operating.

3. In a roll feed, a. drive shaft rotation of which moves material through said roll feed, a clutch member mounted on Said shaft for rotation therewith, a clutch Spider mounted on said shaft adfiacent said clutch member, means for rotating said clutch Spider including a coarse adjustment for controlling motion thereof, the portion of said clutch Spider adjacent said clutch member having an axial groove with tapered sides, said clutch member having a projection With tapered sides adapted to be received in said groove, said groove and said projection constituting a lost motion connection between said clutch member and said clutch Spider whereby rotation of said Spider iS transferred in part to said drive shaft, and a fine 'adjustment for controlling motion of said drive shaft including means for changing the depth to which the projection is received in said groove while said roll feed is Operating.

4. The Structure of clairn 3 further characterized by yielding means interposed between said clutch member and Said clutch Spider bi'asing Said projection away from said groove.

5. In a roll feed, a drive shaft rotation of which moves material through said roll feed, a clutch member mounted on Said Shaft for rotation therewith, a clutch body freely reciprocal around Said shaft, a clutch Spider mounted on said shaft adjacent said clutch member, a gear mounted on and secured to Said clutch body, means for reciprocating Said gear including a coarse adjustment for controlling the motion thereof, said clutch Spider and said clutch body being interconnected whereby reciprocation of said gear and said clutch body in one direction rotate said Spider, a portion of said clutch Spider |adjacent said clutch member having an axial groove with tapered sides, said clutch member having a projection with tapered side walls adapted to be received in said groove, said groove and Said projection constituting a lost motion connection between said clutch member and Said clutch Spider whereby rotation of said Spider is transferred in part to said shaft, and a fine adjustment for controlling motion of said drive Shaft including means for changing the depth to which said projection is received within Said groove while said roll feed is Operating.

6. The structure of claim 5 further characterized in that said means for rotating said gear include a rack bar positioned for longitudinal movement adjacent Said gear.

7. The Structure of claim 6 in which Said coarse adjustment includes an eccentric rotation of which longitudinally moves said rack bar.

8. The structure of claim 5 in which the interconnection between Said clutch body and said clutch Spider include a plurality of grooves around the periphery of said Spider underlying said body, each of Said grooves containing a clutch roller positioned to rotate said clutch Spider upon rotation of said clutch body in one direction.

9. In combination, a feed Shaft, reciprocating drive means therefor, an over-running clutch between said drive means and said feed shaft, coarse adjustment means for varying the excursion of the drive means and fine adjustment means independent of the coarse adjustment means for varying the extent of response of the feed shaft to the over-running clutch.

10. In combination, a drive shaft, reciprocating drive means therefor, an over-running clutch between said shaft and drive means, coarse adjustment means for varying the extent of said reciprocation, and a fine adjustment means including a lost motion connection for varying the response of said drive Shaft to said over-running clutch.

11. The structure of claim 10 in which said fine adjustment means further includes means for varying the degree of lost motion to change the response of said drive Shaft to said over-running clutch during operation.

12. The structure of claim 10 in which Said lost motion connection includes a clutch member mounted on said shaft for rotation therewith, a clutch Spider mounted on said Shaft :adjacent said clutch member, the portion of said clutch Spider adjacent said clutch member having an axial groove With tapered sides, said clutch member having a projection with tapered Sides adapted to be received in Said groove, said reciprocating drive means adapted to rotate said clutch Spider.

13. The structure of claim 12 in which said fine adjustment means include means for varying the depth to which Said projection is received in said groove while said shaft is turning.

References Cited in the file of this patent UNITED STATES PATENTS 1,887,977 Jensen Nov. 15, 1932 1,909,831 Jensen May 16, 1933 2,841,997 Manst July 8, 1958 FOREIGN PATENTS 761,845 Great Britain Nov. 21, 1956 1,126,832 France Dec. 3, 1956 

